Tumbling machine



Oct 1944 J. E. VETORINO EIAL 2,360,380

' TUMBLING MACHINE Filed Dec. 9. 1942 4 Sheets-Sheet 1 c 17, 1944- J. E. VETORINO ET AL 2,360,380

.TUMBLING MACHINE Filed Dec. 9, 1942 4 Sheets-Sheet 3 Oct. E7, 194%. J. E. VETORINO ETAL 2,360,3'30

'TUMBLING MACHINE Filed Dec. 9, 1942 4 Sheets-Sheet 4 Patented Oct. 17, 1944 UNITED STATES PATENT OFFICE TUM'BLING BIACHINE John E. Vetorino, Fairhaven, and Norman R. Gendron, New Bedford, Mass., assignors to Continental Machinery *'Co., Inc., New Bedford, Mass., a corporation of Massachusetts Application December 9, 1942, Serial No. 468,445

18 Claims.

The present invention relates to tumbling machines, and more particularly to machines for tumbling hides, skins, fabrics and the like during degreasing, washing, or otherwise treating the same. The present application is a continuationin-part of application, Serial No. 365,366, filed November 12, 1940,

In Letters Patent 1,979,237, issued October 30, 1934, to Frank Vetorino, there is disclosed a unitary laundry machine for both washing the laundry and then drying it. The machine comprises a plurality of wash-containing combination tumbler-and-extractor perforated drums or cylinders removably and interchangeably mounted, with their axes horizontal, in individual washing tubs containing washing fluids, The tubs are mounted upon a frame symmetrically with respect to a vertically disposed shaft that is rotatalble by a motor under the control of a positively operating clutch.

In operation, the tubs are filled with washing fluids, and the cylinders are loaded with clothes to be laundered. With the clutch ineffective, the frame that carries the tubs being at this time held stationary by a brake, the motor automatically rotates the cylinders in their respective tubs about their horizontal axes, first in one direction, and then in the opposite direction, a1- ternately. This results in tumbling the clothes in the washing fluids to effect the washing operation.

After the washing cycle has [been completed, and While the cylinders are still rotating, the tubs are drained of the washing fluids; whereupon the brake is released and the clutch is simultaneously rendered effective to rotate the vertically disposed shaft from the same motor. The frame, the tubs mounted thereon, and the cylinders contained in the tubsbecome thus revolved as a unit with the vertically disposed shaft about the axis thereof to extract by centrifugal action the washing fluids still remaining in the laundry after the draining.

Because the application of the clutch, at the commencement of the extracting cycle, is quite sudden, notwithstanding that it slips frictionally to some extent, there is a tendency for the rotation of the cylinders about their horizontal axes to become stopped dead short immediately upon the commencement of their revolution about the vertical axis. This sudden transition, coupled with the fact that the machine is quite heavy, introduces considerable shock and jar.

The machine was thereforere-designed in order to reduce this shock and jar.

According to the.

operation of the re-designed machine, disclosed in Patent 2,235,467, issued March 18, 1941, to the said Frank Vetorino and John E. and Joseph E. Vetorino, the load was reduced by eliminating the frame that carried the rotatable tubs, and

' by mounting the combination tumbler-and-extractor cylinders permanently at opposite ends of a horizontally disposed carrier shaft. The positively driven clutch of the machine of Patent 1,979,237, moreover, was replaced by a centrifugally acting clutc'h. that did not become effective immediately upon the release of the brake. The centrifugally acting clutch comprised a plurality of clutch shoes that were forced by centrifugal action into engagement with a rotating clutch flange. One reason for the adoption of the centrifugal clutch was thatthe re-design of the machine required the re-location of certain intermeshing bevel gears of the original machine, and this re-location, it was thought, would interfere with the drive of a positively acting clutch.

In this re-designed machine, the rotation by th motor of the cylinders about the axis of their horizontally disposed carrier shaft was continued for a brief period of time after the release of the brake. During this brief time period, when neither the brake nor the clutch was effective, not only did the motor continue to rotate the cylinders about their common horizontal axis, but it also commenced to revolve the cylinders with their carrier shaft as a unit about the axis of the vertically chsposed shaft, A combined rotation of the cylinders about their horizontal axis and revolution about their vertical axis was thus introduced. The revolution about the Vertical axis was at first slow, but later at gradually increasing speed. The rotation of the cylinders about their horizontal axis gradually decreased, furthermore, as their revolution about the vertical axis increased. When the clutch finally became effective, upon the machin attaining sufficient speed of revolution about the vertical axis, therefore, it was with considerably less shock and jar than was the case with the machine of Patent 1,979,237.

Once this speed of revolution was arrived at, it was expected that the clutch would remain effective to revolve the cylinders about the vertical axis, and without any further rotation of the cylinders about their horizontal axis. This exfor the intervals required for the machine to pick up sufficient speed of revolution about the vertical axis to throw out the clutch shoes by centrifugal action turned out to be rather long. There is nothing definite, positive, determinate or dependable, furthermore, in this rather long time of delay; it may be great or small, depending upon the load and other conditions of operation. One is never certain, indeed, as to whether, unless sufficiently heavy loads, the centrifugally acting clutch shoes will really take effect at all, at any time. Under many conditions, these clutch shoes no sooner engage the rotating clutch flange than they let go again, over and over again; thus successively rubbing gently against the clutch flange and then disengaging it, a number of times, but without ever obtaining frictional grip sufiiciently permanent to pick up the load required during the extracting cycle.

Under such conditions, therefore, the theoretically expected cessation of the rotation of the cylinders about their horizontal axis does not take place, even after the clutch shoes do begin lightly to engage the clutch flange. All that is attained is merely a continuation of the same combined rotation of the cylinders about their horizontal axis and revolution about the vertical axis that obtained before the clutch shoes began to engage and disengage the clutch flange. Pure vertical revolution only of the cylinders, without their accompanying horizontal rotation, is seldom attained.

An object of the present invention is to provided a new and improved unitary machine of the character disclosed in the said Letters Patent for both tumbling the contents of the cylinders in solvent or other liquid, in order to wash, degrease or otherwise treat the contents, and then drying the same.

Another object is to transfer, at will, positively, at any speed of operation of the machine, and at any desired time, but without shock or jar, from a pure rotation of the cylinders about their horizontally disposed axis to a pure revolution of the cylinders about the vertically disposed axis.

A further object is positively to control the length of the time period that shall elapse between the moment when the cylinders commence revolving about the vertically disposed axis and the movement when they cease rotating about their horizontally disposed axis.

Other and further objects will be described hereinafter and will be particularly pointed out in the appended claims.

With the above ends in view, a machine has been devised of a nature similar to that of the said Letters Patent, but in which the time when the clutch becomes effective, in order to reduce shock and jar, may be controlled either automatically, or manually, or both, as circumstances may require. According to a feature embodied in the preferred machine that is illustrated and described herein, this time may be controlled by providing for a time sequence of operation of the brake and the clutch, or by a suitable adjustment of the clutch slip, so as to permit slippage to a predetermined degree, or both.

The invention will now be more fully described in connection with the accompanying drawings, in which Fig. 1 is an end elevation of a machine embodying the present invention, in preferred form, parts being broken away and other parts being shown in transverse vertical section, for clearness; Fig. 2 is a horizontal section taken upon the line 22 of Fig. 5, looking downward, in the direction of the arrows; Fig. 3 is a side elevation similar to Fig. l, partly in longitudinal vertical section upon the line 3-3 of Fig. 1, looking in the direction of the arrows; Fig. 4 is a fragmentary plan, with upper parts of the machine removed, showing the supporting annulus for the brake-disengaging member and related parts; Fig. 5 is a fragmentary side elevation similar to Fig. 3, but upon a larger scale, and showing in section many parts shown in elevation in Fig. 3; Fig. 6 is a section upon a larger scale, of parts shown in Fig. 5; and Figs. 7 and 8 are sections taken upon the lines 'I'I and 8-8, respectively, of Fig. 6, looking in the directions of the arrows.

The illustrated form of the present invention comprises an upright outer stationary cylindrical frame or casing I that may constitute a cleaning-and-drying or washing-and-drying or degreasing-and-drying chamber or the like. A pair of angle-iron reinforcing bands 2 and 3 are shown suitably secured to the casing I around its upper and lower ends, respectively. The up-- per end of the casing I is surmounted by a circularly formed dome-shaped covering top 1, provided around its lower edge with an angle-iron reinforcing band 8, shown bolted at 81 to the flange 2. A circular cap-like clutch housing 3| is secured to the upper surface of the cover I by means of bolts 33 extending through a bottom edge flange 32.

An outwardly opening circular door II is hinged at I2 to the casing I. The door II closes on an annular flange I3 that surrounds a circular-door opening I4 provided in the casing I. A pair of keeper bolts I5, hinged at 88 to the flange I3, may be swung into bifurcated edge lugs I6 on the door II to force the door II tight against the flange I3.

Within the casing I, at opposite sides thereof, there are disposed inner combined tumblerand-extractor drums or cylinders I'I, each provided with concavo-convex, oppositely disposed, front and back side or end walls I8 and I9. The back end walls I9 are shown arching inwardly and the front walls I8 outwardly. With the exception of the back Walls I9, the cylinders I! are shown perforated at 24. The cylinders H are detachably secured together coaxially, in back-to-back spaced-apart relation, at the re spective ends 2I of a short horizontal transversely disposed shaft 20, that is positioned intermediately between the cylinders. By reason of this construction, each cylinder acts as a counterweight, to counter-balance the other on the shaft 29. The shaft 20 is tapered at its ends 2| to fit into axial sockets 22 provided on the inwardly arching back Walls I9. cylinders I! are clamped to the ends of the shaft 20 in any suitable manner, as by means of bolts 23 that pass through the back walls I9 of the respective cylinders and into the shaft 20. Each cylinder I! is thus carried by the shaft 20 at its inner end wall I9.

Each cylinder I1 is provided with an annular door frame 25 that is suitably secured concentrically in the front wall I8 of the cylinder. Each cylinder I1 is provided also with a perforated circular door 21, preferably arched inwardly of the cylinder, and fitted within the door frame 25. The door 21 may be detachably secured in the frame 25 by means of an edge lug 28, that fits in a grooved inner edge 26 of the frame 25, and a pair of latch bolts 29. The bolts 29 are The- .on 4 face that, as hereinafter morelfullydescribed, .the".

open-ended cylinders .l I are loaded and. unloaded withehides skins, laundry and thelik'e; .The cylinders may be rotated. about. the aii's of their horizontally disposed shaft 20, to turn bleutheir contents, thereby to. effect a Washing", cleaning, degreasing. or other operation They may. also be revolved a aunit aboutthe vertical axis o f the casing I,,t'o.extractliquidfrom'the tumbled contentsv by centrifugalv action. This vertical axis though between the-cylinders] I], is dispos,ed eXternallyof each cylinder, individuallyenear the inner end wall,l9 thereof.. The drive forefiectingeither or bothof these aetions is obtained from a pulley 34, shown driven continuously. from an, electric. motor 4|, through the .medil mof a belt 44, The pulley .34 iswhori zo tally disposed concentrically in the upper, portion of the housing 3 l.,.and. is rotatable a rially of the casing I and the. housing 3| .on a bolt-likearbor, v3B. The arbor] 38', vextended throughthe topof the housing 3|, is fixedon the upper end thereof by a nut 39 that is. covered by a (3 3135441, suitably fixed .tothe housingBL,

Ifh e. pulley-34 ,is provided, with .2, depending circumferential skirt that constitutes a clutch flange 35.. A bevel gear 36, disposed within, the pulley 34, is D10Videdwith a hub that is keyed, as ushown at 3'l,..in the hub of the pulley 34. The bevel gear 35 is thus rotated from the puly.

. .1 The electric rnotor 4I- is shown bolted at 42 te a. bracket S that extendsv frornflone side of the cover 'l Thebelt .44 extends through a suite able throat 19, providedin the. same side of. the housing 5|, over- ,the pulle y .34 and a pulley. 45 that is fast on. the uprightly, disposed armature shaft 43 of the motor-4L. .The belt 441s shown as of the ;ml 11tip1':ba i1d type, andthe pulleys 34 and i5 are grooved suitably to receive this type ofbeltk .J. v fiat hollow carriergearcasing 46..is up.- standingly disposed; centrally. of the shaft 20, for. revolution within, and about. the said ..ver tical axis of,.the casing I. The cylinder-carry.- ing shaft 25 is journaled in,,and extendsthrough, ball-bearing .a ssemblies 55. ..'I he ball-bearing assemblies 55 are suitablyfittedand secured in annular flanges 86 of the sides of the gfearcasing 46. ,The tapered ends 2| of the shaft 20 extend beyond the bearings 55 inwhich theshaft Zilis journaled. The gear casing .46, therefore, functions as a carrierfor, the cylinder-carrying shaft z fl, with theeylinders I! disposed on oppositesidesof the carrier ,46. v a

The shaft Zllis thus not onlyrotatable about itsown axis,.but it is v also revoluble.- in.,unison with the gear casing 46 in which iteism ou'nted,

' and the cylinders l1 carriedthereby, about the said vertical axis of ,the casing I.

I'he lower endpof .thegear casing 46, as shown more. particularly in Fig. 5, is provided. with a step-shaped trunnionAB that extends through. a suitable stuffing box .49, so as to .be. supported or journaled in. a suitable end-thrustbearing-as sembly 5 I, .The stufiingrbox 49 is bolted at .50 in a eentrally, disposed opening or aperture 6 of a bottom wall 4 of the. casing 1, that isshown reinforced by radial flanges 5, and the bearingas'jse b1y.5l' is bolted at 52' to and beneath this bottom Wall'4.

...Thelupper end of the gear casingg 46 is provided'witha tubular neck 92 that, as shown more particularly, in Fig. 6, extends upward through a.centrally disposed aperture 90 in the upper wall ,99 of the cover I, and through a ball-bearing assembly Bil -contained in a tubular housing 5.3, into ,the'lowenportion of the housing 3|. The

hdus'irig' 5,3,, with the ball-bearing assembly 89 therein, is shown held to the cover I by bolts 54 that ,extend through a flange 98 of the housing 53','intothe upper wall 990i the cover l. A skirt [02, depending from a circular flange-like or disc-like brake plate4'l, rests on the upper surface of the housing'53. a M M a g v A A wall I flll welded in place toclose the upper end of the neck 92; is provided with a keyway I (g1, shown rnore clearly in Fig. a. The depending skirt ")2 is provided with a cooperating keyway I03. A key 10 4', disposed in the key-ways I'B l aindlflfiahdbolts J05, extending through the skirt: I02 and the wall I00, hold the gear casing fixed to the brake plate41.

'Ifh'e bralg'e plate 41 is'thus concentrically fixed inthe lower .portion of the housing,3l at the upper end ofthe gear casing46. The upper surfaee at the p1at 41 carries an annular brake di 38 for holding the gear casing 46 against ution about the vertical axis. The positien of the brake disc [38 upon the plate 41 may be adjusted by meanslof bolts I39. I

An; annular bushing or sleeve I23 and lugs LL9 stand fixedly from the brake plate 41in the houjsin'g 3 l below t e pulley 34. The axis of the bushing I23 coincides with the vertical axis of the housing I; it is therefore concentric with thebrake disc I38. A transversely disposed crQss shaft 59' extends horizontally through, and is f x'ed in the upper ends of, the lugs I I9, 111 si'de'the clutchflange 35. h repair of segmentalshaped clutch shoes 10 are siidably mounted on oppos ite ends of the shaft 59 a The clutch shoesllo are tlri'u's fizied to the cylinders H to communicate their revolution thereto. V

Li'ght normally ineffective coil springs II are sleeved on the respective opposite ends of the shafteil; between the clutch shoes 10 and the lugs) it. The springs l l tend yieldingly to actuate clutch shoes luoutwardly to actuate their outerfaoe's into cooperating clutching en'- gagementwiththe inner face of the rotatable clutch flange 35. as illustratedvrnore particularly During such elutching engagement. the clutch shoes 10 rotate with the rotatable clutch flange 35. The clutch flange 35 thus constitutes the continuously driven rotatable clutch member, andthe clutch shoes Hi thecooperating clutch member of. the clutch. The clutch is ef fectiveto revolve the cylindersll as a unit about the vertical axis when the clutch shoes 10 engage the clutch flange .35. p n v Inl the normal position of the clu'tchshoes 19, in which the .clutch is normally ineffective, the Clutchshoes luarereleased from clutching en a ementwith the clutch flange 35 The clutch shoes 10 may be released from clutching engagement. with the clutch flange 3 5 by. sliding them inwardly on the shaft BQ, as hereinafter described. A smallvsprocket wheel 'l3 is mounted on, so asto rotate. with, the shaft 6 9, and.is confined against lateralmovement between the lugs H9. Av bevel. gear .15, that is. fast on the hub of the sprocket wheel 13, meshes with the bevel gear 36, so as to be driven thereby. A large sprocket driving gear wheel 16, centrally mounted within the gear casing 46 upon the shaft 20, between the ball-bearing assemblies 55 and between the cylinders I1, is driven from the sprocket wheel 13 by means of a sprocket chain 11. The sprocket chain 11 passes downwardly, out of the casin 3I, into the casing I, through the housing 53. It passes not only over the sprocket wheels 13 and 16, but also, as shown more particularly in Fig. 1, over a pair of opposed idler sprocket wheels 18 that are suitably mounted in the gear casing 46, upon opposite sides of and adjacent to the neck 92 of the gear casing 46.

The shaft 2|, upon which the cylinders I1 are mounted, is thus rotated from the pulley 34 that carries the driven clutch member 35, at a time when the clutch is ineffective, by means of a planetary gear drive comprising the gears 36 and 15, the sprocket wheel 13 driven thereby, the sprocket chain 11 and the sprocket wheel 16. The drive is at this time, not from the driven clutch member 35, but rather from the bevel gear 36, both of which are rotated from the continuously rotated pulley 34 by the motor 4|.

An important function of the bushing or sleeve I23 is to centralize an annular brake-disengaging member I21 and a supporting annulus I33 therefor along the vertical axis of the casing I. The brake-disengaging member I21 concentrically encircles the upper portion of the bushing I23, above the supporting annulus I33 and below the shaft 69 and the clutch shoes mounted thereon. The supporting annulus I33 concentrically surrounds the lower portion of the bushing I23, between the plate 41 and the brakedisengaging member I21.

As illustrated more particularly in Fig. 5, the brake-disengaging member I21 is provided on its inner peripheral edge with an internally beveled upstanding annular flange I29. Anti-friction ball members I32 are carried at the outer ends of studs I30 that extend outwardly from hubs I3I of the clutch shoes 10. The flange I29 and the studs I36 constitute coacting camming devices.

The annulus I33 is rendered resiliently movable, to yield vertically up and down, to a small extent, by mounting it upon a plurality of tempered resilient spring-metal supporting pins I34,

that extend radially outward of the annulus I33, into tapered plugs I35. The tapered plugs are threaded on the outer ends of the pins I34, to render them slidably adjustable radially on these pins in the housing 3I. the annulus I33 and the brake-disengaging member I21 from rotating with the plate 41.

Both the annulus I33 and the brake-disengaging member I21 are serrated. On its upper base, the annulus I33 is provided with cam notches I 31 that are adapted to engage coasting cam lugs I36 upon the lower face of the annular brake-disengaging member I21.

The brake-disengaging member I21 is movable back and forth, through a small angular extent, about the axis of the bushing I23, by means of a hand lever I28 that extends radially outward of the brake-disengaging member I21 through a slot I26 in the clutch housing 3I.

When the hand lever I28 is manually actuated clockwise, from the full-line toward the normal dotted-line position of Fig. 2, the brake-disengaging member I21 is likewise actuated clockwise to a corresponding angular extent. By reason of the engagement between the coasting cam The pins I34 prevent lugs I36 and cam notches I31, the brake-disengaging member I21 is at the same time, however, yieldingly carried upward, as viewed in Figs. 3 and 5, to a small extent, on the cam notches I31.

The brake-disengaging member is thus operable in two directions; angularly, and by a vertical movement of translation. The movement of translation, moreover, automatically accompanies the angular movement, by reason of the coaction of the cam lugs I36 and the cam notches I 31.

During the combined clockwise and upward movement of the brake-disengaging member I21, in response to the actuation of the lever I28 from the full-line toward the dotted-line position of Fig; 2, the beveled flange cam I29 will engage the anti-friction ball members I32 to cam the clutch shoes 10 inward, in opposition to the action of the springs 1I This will effect disengagement of the clutch shoes 10 from the clutch flange 35 of the pulley 34. The cam notches I31 may be thus caused to cooperate with the cam lugs I36 during the rotation of the rotatable clutch member 35, to cause the cam I29 upon its upper side to disengage the clutch shoes 10 from the clutch flange 35, to hold the clutch shoes 10 against further revolution. The brake-disengaging member I21 thus constitutes a clutch-disengaging member, as well.

After the clutch shoes 10 have traveled their maximum distance inward, and the brake-disengaging member I21 has been raised to the highest point possible, further pressure on the lever I28 in the same direction, toward the dotted-line position of Fig. 2, will result in forcing the annulus I33 downward to a small extent, in opposition to the force resiliently exerted at this time by the pins I34. When the annulus I33 is thus cammed downward to its lower position, following upon the upward movement of the brake-disengaging member I21, its lower face is forced into braking engagement with a suitable brake lining I 49, provided upon the upper face of the annular brake disc I38.

As hereinafter more fully described, the washing or degreasing operation is performed during the rotation of the cylinders I1. After this operation has been completed, and while the cylinders I1 are still rotating, the solvent is drained off by opening a suitable drain plug 9|, in the bottom wall 4. The time has now arrived to actuate the handle I28 in the opposite direction, from the dotted-line position toward the full-line position of Fig. 2, in order to effect extraction, by centrifugal action, of the solvent still remaining in the goods after the draining of the solvent.

When the hand-lever I28 is thus manipulated from the dotted-line toward the full-line position of Fig. 2. the brake-disengaging member I21 will be actuated counterclockwise. The cam lugs I36 will ride down on the cam notches I31, which will permit the brake-disengaging member I21 to become lowered at the same time that it is actuated counter-clockwise. The springs 1I will then thrust the ball members I32 outward against the beveled flange I29, to actuate the clutch shoes 10 into clutching engagement with the flange 35 of the driving pulley 34, as illustrated in Fig. 5. At the same time, the annulus I33 will be actuated to its upper position, in response to the resilient action of the metal pins I 34, thereby to disengage the brake lining I40 on the brake disc I38.

In operation, let it be assumed that the motor M is disconnected from the line. The cylinders Il may be loaded, through the doors 2! in their front open ends. To this end, the casing 46, with the cylinders I! carried thereby, is first revolved about its vertical axis through a fractional turn, until the door 2! of one of the cylinders ll becomes alined with the casing-door opening I4. This door 21 is then detached from its cylinder and removed through the door opening I4. That cylinder is then loaded with skins, hides, laundry, or the like. The casing 46 is then revolved through I80 degrees further, or until the other cylinder door 21 becomes alined with the casingdoor opening I4. This other cylinder is then similarly loaded.

The casing I is then filled to the desired level with the solvent or other liquids that are to be used for the purpose of degreasing the hides or skins, or Washing the laundry, or otherwise treating the contents of the cylinders II. These liquids may be admitted through an inlet pipe 80, air being at the same time exhausted through an outlet pipe BI. The machine is now ready for operation. All that is necessary is to connect the motor 4| to the line. This effected, the motor rotates the pulley 34 and the bevel gear 36 that is fixed thereto.

Three difierent operations will be described, depending upon whether the lever I28 occupies the normal dotted-line, ineffective position, or the full-line efiective position of Fig. 2, or a position in between (not shown). The pulley 34 and the bevel gear 36 will be assumed to be continuously driven from the motor 4| in all three positions of the lever I28.

When the lever I28 occupies the normal dotted.- line position of Fig. 2, the brake-disengaging member I2I occupies its upper position, in which the clutch shoes 10 are disengaged from the flange 35, so that the clutch is ineffective, and the annulus I33 its lower position, in which it engages the brake disc I38. The cylinders H are therefore free to rotate about the axis of the horizontally disposed cylinder-carrying shaft 20; and the brake disc I38, in this normal position, prevents their revolution, with their carrier casing 43, about the vertically disposed axis of the carrier casing 43. The normal dotted-line position may therefore be termed the cylinder-rotation position, because the drive of the cylinders from the driven clutch member 35, when the lever I28 occupies this position, is constituted of a pure rotation about the horizontal axis. The full-line position may similarly be termed the cylinderrevolution position, because the drive of the cylinders from the clutch members 35 and I0, when the lever I28 occupies this position, is a revolution of the cylinders about the vertical axis. In the intermediate position (not shown) of this lever I28, the connection of the driven cylinders II to the driven clutch member 35 is such that a combined movement of rotation about the horizontal axis and revolution about the vertical axis is imparted to the cylinders.

Referring first to the operation that takes place when the lever I28 occupies the dottedline, or rotation, position of Fig. 2, in this normal position, the brake is effective to prevent revolution of the carrier 46 and the cylinders I! carried thereby, and the clutch is ineffective. The rotation of the bevel gear 36 is converted into rotation of the bevel gear I5 that meshes therewith, and of the horizontally disposed shaft 69 upon which the bevel gear I5 is mounted. The resulting rotation of the sprocket wheel I3 is communicated to the sprocket chain 11, and

this effects rotation of the sprocket driving wheel I6. The rotation of the sprocket wheel I5 is communicated to the shaft 23 and to the cylinders I! carried thereby. In this dotted-line position of the lever I28, therefore, the drive from the pulley 34, the bevel gears 36 and I5, the sprocket wheels I3 and I6, and the sprocket chain II is transmitted to the shaft 20 to rotate the cylinders II, with the horizontally disposedshaft 23 to which they are secured, in unison about the axis of this shaft 20, but they are at this time prevented from revolving about the vertical axis. The cylinders II become thus rotated about their horizontal axis at a time when they are braked against revolution about the vertical axis.

This rotation of the cylinders results in tumbling or agitating the laundry, hides or skins in the said solvent fluids, which may effect the washing of laundry, or the degreasing of hides or skins, or other desired treatment. It is desirable, for such purposes, during the rotation of the cylinders II, to reverse their direction of rotation at the end, say, of each six complete rotations. This reversal of the direction of rotation of the cylinders tends to spread out their contents, thus preventing bunching or snarling thereof.

This reversal may be effected automatically by mechanism that is not illustrated, because well known; this mechanism may, for example, comprise an automatically operating switch for controlling the motor 4i under the control of a double-acting main switch that is closed when the lever I28 occupies its dotted-line position.

For the purpose of extracting, though other uses are also contemplated, the invention provides also for transmitting the drive from the clutch flange 35 'of the pulley 34 to the gear casing 46, thus to revolve the casing 46 and the cylinders IT in unison about the vertical axis of the casing I.

When the lever I28 occupies its full-line, or

I revolution, position of Fig. 2, it may close another main switch (not shown) for effecting the operation of the motor 4| in the same direction throughout, without reversal. At this time, the brake-disengaging member I2! occupies its lower position, to permit the clutch shoes III to engage the clutch flange 35, as illustrated in Fig. 5; and the annulus I33 occupies its upper position, out of engagement with the revolution-preventing brake disc I38. The brake disc I38 is therefore released, or rendered ineffective, rendering the gear casing 46, with the cylinders II carried thereby, free to revolve about its vertical axis. Assuming the clutch to be fully efiective at this time, Without slip, the drive will be transmitted from the flange 35 of the pulley 34 directly to the clutch shoes IS. The consequent rotation of these clutch shoes III will effect revolution, about the said vertical axis, of the shaft 69 and of the lugs II9 on which it is mounted. This rotation of the lugs IE9, in its turn, is communicated to the brake plate 4?; and since the brake plate 41 is fixed to the gear housing 46 by the key I04, the housing 46 becomes revolved about the vertical axis, also. In this position of the lever I28, therefore, the drive is communicated directly from the flange 35 of the pulley 34, through the clutch shoes I0, solely to the gear casing 45 and the parts carried thereby, the bevelgears 36 and I5 acting at this time as though they were rigidly locked together to revolve as a unit about the vertical axis, without relative rotation, and without the bevel gear I5 turning on its own axis. Under these conditions, the casing 46, together with the cylinders I1, and the other parts carried thereby, including the sprocket wheel 13, the cross-shaft 69, the clutch shoes I mounted thereon, and the brake plate 41, will revolve as a unit about the vertical axis, in the same direction throughout, without any rotation of the cylinders I'I about their horizontal axis.

It is now in order to consider what takes place at an intermediate time, after the lever I28 has been actuated out of its dotted-line position, but before the pure revolutionbefore described takes place. For purposes of clarity of explanation, let it first be assumed that the handle I28 is maintained in an intermediate position (not shown) between the full-line and the dottedline positions of Fig. 2. In this intermediate position, both the clutch and the brake are ineffective; the clutch shoes "I0 do not effectively engage the flange 35, and the annulus I33 does not effectively engage the brake disc I38.

Because the clutch is ineffective, the cylinders I'I. will still be rotated about their horizontal axis from the driven clutch member 34 through the bevel gears 36 and I5, the sprocket gear 13, the sprocket chain I1 and the sprocket gear I6. The inertia of the cylinders I! with their loads, however, will tend to oppose the rotation of the cylinders I! about their horizontally disposed axis. There will therefore be a tendency for the gears 36 and I5 to become locked against relative rotation to some extent. This tendency will not now be opposed, however, because the brake is likewise ineffective. There will consequently result a part rotation of the bevel gear about its own axis from the bevel gear 36, and a part revolution of these bevel gears 36 and 15 as a unit about the vertical axis. As a consequence, there will take place a combined rotation of the cylinders I! about their horizontal axis and revolution of the cylinders about the vertical axis, this combined rotation and revolution being both effected from the rotation of the bevel gear 36 alone, under drive from the motor II, and without any engagement of the clutch shoes IB against the clutch flange 35, and resulting solely from the inertia of the cylinders I1 and their loads.

During this combined rotation of the cylinders about the horizontal axis and revolution about the vertical axis, a gyroscopic effect is introduced that enables the contents of the cylinders to become automatically redistributed. Even though the loads on the two cylinders be unequal, therefore, they will so re-arrange themselves as to cause the cylinders and their loads to become very evenly balanced. This balance prevents uneven centrifugal stress from straining or damaging the machine during the extracting cycle.

At first, the speed of rotation of the cylinders about their horizontal axis will be large, and their speed of revolution about the vertical axis small. The speed of revolution, however, will gradually increase and that of rotation will gradually decrease. When the speed of revolution becomes sufliciently great, the lever [28 may be actuated from the intermediately disposed position (not shown) to the full-line position of Fig. 2. The clutch shoes ID will thus be caused to grip against the clutch flange 35 at a time when they are already revolving about the vertical axis at a speed more or less approaching the speed of the clutch flange 35 itself. The clutch shoes I0 will therefore effect their clutching engagement against the clutch flange 35 with a minimum of shock and jar. From that time on, moreover, the clutch shoes III will assure pure revolution of the cylinders I1. and their loads about the vertical axis, and without any further rotation of the cylinders about their horizontal axis. The rotation of the cylinders I! around the horizontal axis is thereafter completely stopped, and the sole motion is a revolution about the vertical axis. This condition will obtain as long as the clutch remains effective.

The above description has been upon the supposition that the lever I28 is maintained in its intermediately disposed position (not shown),

following upon the completion of the washing or degreasing cycle, until the machine picks up speed. In actual practice, it is not necessary that the lever I28 be held in the intermediately disposed position. It may be actuated directly from the dotted-line to the full-line position of Fig, 2, and the same effect will take place.

This is because, upon the actuation of the lever I28 from the dotted-line toward the full-line position of Fig. 2, the brake I38 releases before the clutch shoes I0 become effective. Even though the clutch lever I28 be actuated directly from the dotted-line position to the full-line position of Fig. 2, therefore, there will be a brief interval of time following upon the release of the brake, and before the clutch shoes become effective, during which the brake and the clutch are both ineffective, and during which the combined rotation and revolution of the cylinders I! takes place under drive from the motor, in the same manner as before described. Because of the existence of this brief period of time subsequent to the pure rotation of the cylinders and prior to their pure revolution, there is the same tendency as before described to reduce shock and jar.

Such shock and jar as might still be introduced by too early engagement of the clutch shoes Ill with the clutch flange 35, moreover, may be further minimized by suitable adjustment of the tension of the springs II, and of the degree of inward and outward movement of the clutch shoes III, to ensure that the clutch shoes I0 shall not grip too firmly to start out with against the clutch flange 35, but shall grip rather with a slip action until after a predetermined time delay. Further rotation of the cylinders II about their horizontal axis may thus be prevented at any desired time, during the combined rotation and revolution of the cylinders, after the brake has been rendered ineffective.

Owing to the before-described inertia of the cylinders I1 and the loads contained therein, the clutch shoes III will not immediately clutch positively against the flange 35 as soon as they engage this flange, but they will slip to some extent. Owing to this slip, the cylinders I! will continue to rotate to some extent about the axis of the horizontal shaft 20 at the same time that they revolve about the vertical axis, in the same way as already explained. The rate of slippage gradually decreases until, finally, the clutch shoes 10, under the action of the springs H, become enabled to grip the clutch flange 35 positively with suflicient force. Thereafter, the springs II will maintain the clutch shoes III effective. From that time on, therefore, there will be no further rotation of the cylinders I! about the axis of the horizontal shaft 20, but the entire motion of the cylinders II will be a revolution about the vertical axis.

. the cylinder To adjustthe time delay introduced by this slippage of the clutch from the moment that the clutch shoes'll) engage the clutch flange 35 until the cylinders cease rotating about their horizontal axis, threadedly adjustable stops 93 may be provided at the upper ends of the lugs II9, as illustrated more particularly in Figs. and 6. These stops may engage the inner faces of the respective .clutch shoes I0 to prevent their inward movement beyond the extent desired. Unauthorized or accidental adjustment of the stops 93 may be prevented by means of check nuts 95. The positions of adjustment of these stops 93, of course, will determine the dottedline position of the hand lever I28, shown in Fig. 2 they will also ensure that the tension on the springs ll shall be such as to provide the proper amount of tension and compression of the springs H for smooth operation of the clutch in 'changing from the rotation of the cylinders to their revolution. The presence of the stops 93, furthermore, makes it possible to adjust the lever I28 to its dotted-line position without fear of causing damage to the springs H or other parts of the machine, as by imposing undue strain upon the springs H, or upon the brake disc 33. The last-named safety feature also ensures proper adjustment of the brake disc I38 without the necessity of re-adjusting the bolts 539 as the machine continues in use. The stops $3 may be readjusted as oocasion demands, so as to prevent excess slippage of the clutch, such as might be introduced by wear of the clutch parts and their lining.

To the attainment of similar ends, the antifriction ball members I32 may be rendered adjustable on their hubs l3I, as by means of threads 96, and they may be locked in'adjusted position in any desired way, as by means of set screws 97, shown in Fig. 2. The positions of adjustment of the ball members I32, like the positions of the stops 93, control the degree of inward movement of the clutch shoes I0, thereby likewise controlling the time of slip of the clutch shoes I0 against the clutch flange 35.

This time of slip may be adjusted to a value as low as a few seconds, or to a value as high as nearly a minute or more. Too short a time of slip, as before explained, introduces strain and jar, but too large a time involves unnecessary time lost in the operation of the machine. A total time delay of about 2'1 seconds has been found, in practice, to be very suitable in most cases, but this may often be effectively increased up to about 45 seconds.

When the cylinders I1 have been revolved sufficiently about the vertical axis to complete the eXtracting cycle, the hand lever I28 may finally be returned to its normal dotted-line position once more. This restores the brakedisengaging member I21 to its upper position, and the annulus I33 to its lower position. The clutch shoes Ill, therefore, become again disengaged'from the clutch flange 35, and the annulus I33 becomes again actuated into engagement with the brake lining I40 on the brake disc I38. The revolution of the gear casin 46, with IT and the other parts carried thereby, will thereupon become first retarded, and then ultimately stopped. Meantime, owing to continued rotation of the pulley 34 by the belt 44, the drive becomes again automatically transmitted from the bevel gear 36 to the bevel gear '15 and thence, by the sprocket-and-chain mechanism, to the shaft 20, thus restoring the previously described rotation of the cylinders I! about the horizontally disposed axis of the shaft 20. v

For a time, therefore, there will again be a combined rotation of the cylinders about their horizontal axis and revolution about the vertical axis. This results in tumbling the clothes still further. This is advantageous, because the goods in the cylinders become opened out thereby, permitting them to fall away from the doors 2?, against which they have been pressed by centrifugal action during the extracting cycle, when the cylinders were revolving about the vertical axis. Unloading of the goods in the cylinders becomes thus facilitated.

The revolution of the cylinders I! about their vertical axis should be stopped, at the completion of the extracting cycle, in such position as to register Or aline the doors 2! of the cylinders il with alined inlet and outlet air pipes Ifi. Hot air under pressure may then be blown into the cylinders through these doors 2 while the cylinders are still being rotated about their horizontal axis. Because the contents of the cylinders have already fallen away from the doors 21, the hot air becomes enabled to penetrate into the clothes in the cylinders ll. Most of the residual solvent remaining in the goods after the draining is removed from the goods during the extraction cycle; the hot-air blast removes the remainder, in order to complete the drying.

This final combined rotating-and-revolving movement of the cylinders, subsequent to the extracting operation, may be effected at a time when the power from the motor 4! is shut off, and wholly by the inertia of the moving cylinders and their loads; the motor may be disconnected from the line. Though no powe is at this time obtained from the motor, the machine will continue its. combined rotation and revolu tion of the cylinders by its own inertia if the motor switch is opened while the cylinders are still revolving. During the continued revolution of the machine about the vertical axis by its inertia, there is introduced also a rotation of the cylinders about their horizontal axis, caused by relative movement of the gears 36 and I5, as before described. The gears 36 and I5 lock to some extent, to permit revolution of the cylinders, but they rotate also with respect to each other to some extent, to permit rotation of the cylinders.

A machine is thus provided by the present invention that positively, and without fail, will perform the functions demanded of it, and exactly at the times when so demanded. When the hand lever I28 occupies its extreme normal dottedline position, the motion of the cylinders I! will be a pure rotation about their horizontal axis, revolution about the vertical axis being, at this time, prevented by the annulus I33 engaging the brake lining I40 upon the brake disc I38. Upon the actuation of the lever I28 to its extreme fullline position, a suitable time interval will ensue, the length of which may be adjusted, during which there will be combined rotation of the cylinders about the horizontal axis and revolution of the cylinders as a unit about the vertical axis. The speed of revolution about the vertical axis gradually increases, and the rotation about the horizontal axis gradually decreases, until the speed of rotation about the horizontal axis stops altogether, at a time determined by the adjustment, The sole motion thereafter is a pure revolution only of the cylinders about their vertical axis as a unit, without horizontal rotation. By actuating the lever I28 to an intermediate position, where such may be desired, it is possible also to obtain combined rotation of the cylinders about the horizontal axis and revolution about the vertical axis, until the machine runs down by its inertia.

Modifications will occur to persons skilled in the art, and all such are considered to fall within the spirit and scope of the invention, as defined in the appended claims.

What is claimed is:

1. .A machine of the character described having, in combination, a plurality of substantially axially alined cylinders rotatable about their axis, a brake for preventing the revolution of the cylinders during their rotation, means for simultaneously rotating the cylinders about their axis and revolving the cylinders about another axis between the cylinders, and means operable after the release of the brake for preventing the rotation of the cylinders during their revolution.

2. A machine of the character described having, in combination, a plurality of substantially axially alined cylinders, means for simultaneously rotating the cylinders about their axis and revolving the cylinders about another axis between the cylinders, and means for preventing the rotation of the cylinders during their revolution.

3. A machine of the character described having, in combination, a plurality of substantially axially alined cylinders rotatable about their axis, a brake for preventing the revolution of the cylinders during their rotation, and means for first simultaneously rotating the cylinders about their axis and revolving the cylinders about an-' other axis between the cylinders and then effecting revolution of the cylinders without rotation.

4. A machine of the character described having, in combination, a driven clutch member, a cooperating clutch member that may be actuated into engagement with the driven clutch member so as to be actuated therewith, a shaft, bearings in which the shaft is journaled with its ends projecting beyond the respective ends of the bearings, two cylinders each having end walls, the cylinders being carried by the respective ends of the shaft each at one of the end walls, means controlled by the driven clutch member at a time when the cooperating clutch member is disengaged therefrom for rotating the shaft, the said means comprising a planetary gear drive connected to the driven clutch member and including a gear, a sprocket driven by the gear, and a sprocket chain mounted over the sprocket and connected to the shaft between the bearings, means for actuating the cooperating clutch member into clutching engagement with the driven clutch member at any desired time, means connecting the shaft to the cooperating clutch member to revolve the shaft, the bearings and the cylinders as a unit from the cooperating clutch member when the cooperating clutch member is in engagement with the driven clutch member, and means for preventing rotation of the shaft during its revolution.

5. A machine of the character described having, in combination, a casing, a pair of combination tumbler-and-extractor cylinders in the casing, a shaft connecting the cylinders together in fixed axially spaced relation for rotation in unison about a horizontal axis, a shaft-carrier upstanding along the vertical axis of the casing between the cylinders and rotatably mounted in the casing to revolve the shaft and the cylinders in unison about the vertical axis, means for rotating the shaft, means for rotating the carrier, and means for preventing the rotation of the shaft at any desired time during the rotation of the carrier.

6. A machine of the character described having, in combination, a casing, a pair of combination tumbler-and-extractor cylinders in the casing, a shaft connecting the cylinders together in fixed axially spaced relation for rotation in unison about a horizontal axis, a shaft-carrier upstanding along the vertical axis of the casing between the cylinders and rotatably mounted in the casing to revolve the shaft and the cylinders in unison about the vertical axis, a rotatable clutch member, a cooperating clutch member that may be actuated into clutching engagement with the rotatable clutch member so as to be rotated therewith, means controlled by the rotatable clutch member at a time when the cooperating clutch member is disengaged therefrom for rotating the shaft, means for actuating the cooperating clutch member into clutching engagement with the rotatable clutch member at any desired time, and means connecting the carrier to the cooperating clutch member to rotate the carrier.

'7. A machine of the character described having, in combination, a cylinder rotatable about its axis to tumble its contents and revolvable about an axis external to the cylinder to extract liquid from the tumbled contents, means operable to prevent revolution of the cylinder during its rotation, means operable when the preventing means is ineffective for simultaneously rotating the cylinder about its axis and revolving the cylinder about the external axis, means operable during the simultaneous rotation and revolution of the cylinder for preventing the rotation of the cylinder to effect revolution of the cylinder without rotation thereof, and means for controlling the time at which the rotation of the cylinder is prevented during the combined rotation and revolution of the cylinder.

8. A machine of the character described having, in combination, a cylinder rotatable about its axis to tumble its contents and revolvable about an axis external to the cylinder to extract liquid from the tumbled contents, a brake for preventing revolution of the cylinder during its rotation, means operable upon release of the brake for simultaneously rotating the cylinder about its axis and revolving the cylinder about the external axis, a normally ineffective clutch that may be rendered effective during the combined rotation and revolution of the cylinder to stop its rotation, thereby to effect revolution-of the cylinder without rotating it, means for rendering the clutch effective, and means for controlling the time at which the clutch becomes effective.

I 9. machine of the character described havmg, in combination, a plurality of cylinders, means for simultaneously rotating the cylinders about their axes and revolving the cylinders as a unit about another axis, and means for preventing rotation of the cylinders at any desired time (luring their simultaneous rotation and revoluion. I

10. A machine of the character described having, in combination, a plurality of substantially axially alined cylinders, means for simultaneously rotating the cylinders about their axis and revolving the cylinders as a unit about another axis between the cylinders, and means for preventing rotation of the cylinders atany desired time during their simultaneous rotation and revolution.

11. A machine of the character described having, in combination, a shaft, a bearing in which the shaft is journaled and beyond which the ends of the shaft extend, two cylinders each having end Walls, the cylinders being carried by the respective ends of the shaft, each at one of the end walls, means for simultaneously rotating the shaft and revolving the cylinders and the shaft as a unit about an axis at an angle to the axis of the shaft, and means for preventing rotation of the shaft at any desired time during the simultaneous rotation of the shaft and revolution of the cylinders and the shaft as a unit.

12. A machine of the character described having, in combination, a plurality of substantially axially alined cylinders rotatable about their axis to tumble their contents and revolvable about an axis externally disposed between the cylinders at right angles to their axis to extract liquid from the tumbled contents, means operable to prevent revolution of the cylinders during their rotation, means operable when the preventing means is ineffective for simultaneously rotating the cylinders about their axis and revolving the cylinders about the external axis, and means operable during the simultaneous rotation and revolution of the cylinders for preventing the rotation of the cylinders at any.desired time.

13. A machine of the character described having, in combination, a plurality of substantially axially alined cylinders rotatable about their axis to tumble their contents and revolvable about an axis between the cylinders at right angles to their axis to extract liquid from the tumbled contents. a brake for preventing revolution of the cylinders during their rotation, means operable upon release of the brake for simultaneously rotating the cylinders about their axis and revolving the cylinders about the external axis, a normally ineffective clutch that may be rendered effective during the combined rotation and revolution of the cylinders to stop their rotation, thereby to effect revolution of the cylinders without rotating them, means for rendering the clutch effective,

and means for controlling the time at which the clutch becomes effective.

14. A machine of the character having, in combination, a normally ineffective clutch comprising a rotatable clutch member and a cooperating clutch member; means for continuously rotating the rotatable clutch member; a cylinder; a carrier rotatable with the cooperating clutch memher; the cylinder being carried by the carrier so as to revolve during the rotation of the carrier about an axis at right angles to the axis of the cylinder; means connect ng the cylinder to the rotatable clutch member to rotate the cylinder about its axis and to rotate the carrier to effect revolution of the cylinder about the said axis at right angles to the axis of the cylinder; means effective normally, when the clutch is ineffective, to prevent the rotation of the carrier, whereby, normally, when the clutch is ineffective, the cylinder is rotated about its axis from the rotatable clutch member but without being revolved about the axis at right angles to the axis of the cylinder; means for rendering the preventing means ineffective, whereupon a combined rotation about its axis and revolution about the axis at right angles to its axis becomes imparted to the cylinder from the rotatable clutch member; normally ineffective means operable when effective to render the clutch effective and thereafter to maintain the clutch effective; means connecting the carrier to the cooperating clutch member to rotate the carrier from the cooperating clutch member when the clutch is effective; and means operable during the said combined rotation and revolution of the cylinder to prevent its further rotation at any desired time after the revolutionpreventing means has been rendered ineffective, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the cylinder is revolved about the axis at right angles to its axis but without being rotated about its axis.

15. A machine of the character described having, in combination, a normally ineffective clutch comprising a clutch member rotatable'about a first axis and a cooperating clutch member; means for continuously rotating the rotatable clutch member about the first axis; a bevel gear rotatable with the rotatable clutch member about the first axis; a bevel gear meshing with the first-named bevel gear and rotatable about a second axis; the second-named bevel gear being revoluble about the first axis in response to the rotation of the first-named bevel gear when the second-named bevel gear is prevented from rotating about the second axis; the cooperating clutch member being non-rotatable with respect to the second-named bevel gear but being rotatable with the second-named bevel gear about the first axis; a cylinder the axis of which is at right angles to the first axis; a shaft coaxial with the cylinder and upon which the cylinder is mounted; a carrier rotatable with the cooperating clutch member; the shaft and the cylinder mounted thereon being carried by the carrier so as to revolve during the rotation of the carrier about the first axis; means connecting the shaft to the second-named bevel gear to rotate the shaft and the cylinder about the axis of the cylinder and to rotate the carrier to effect revolution of the shaft and the cylinder about the first axis; means effective normally, when the clutch is ineffective, to hold the second-named bevel gear and the cooperating clutch member, together with the carrier, against rotation about the first axis during the rotation of the shaft, whereby, normally, when the clutch is ineffective, the cylinder is rotated about its axis from the rotatable clutch member but without being revolved about the first axis; means for rendering the holding means inefiective, whereupon the second-named bevel gear becomes rotatable about the second axis in response to the rotation of the first-named bevel gear about the first axis to effect a combined rotation of the cylinder about its axis and revolution thereof about the first axis from the rotatable clutch member; normally ineffective means operable when effective to render the clutch effective and. thereafter to maintain the clutch effective; means connecting the cylinder to the cooperating clutch member to revolve the cylinder about the first axis from the cooperating clutch member when the clutch is effective; and means operable during the said combined rotation and revolution of the cylinder to revolve the cylinder and the shaft upon which it is mounted as a unit with the second-named bevel gear about the first axis, thereby to prevent further rotation of the cylinder at any desired time after the holding means has been rendered ineffective, whereby, thereafter, during the effectiveness of the means for rendering and maintaining the clutch effective, the cylinder is revolved about the first axis but without being rotated about its axis.

16. A machine of the character described having, in combination, a casing, a carrier revoluble in the casing about a vertical axis, a shaft horizontally disposed on the carrier in the casing, two cylinders in the casing each having two end walls one of which is open, the cylinders being fixed to the respective ends of the shaft with their axes horizontally alined with the axis of the shaft, means for rotating the cylinders about their alined axes and for rotating the carrier about the vertical axis to revolve the cylinders in the casing, a brake for preventing rotation of the carrier to efiect rotation of the cylinders about their alined axes without revolution of the cylinders about the vertical axis, means for releasing the brake to effect a combined rotation of the cylinders about their alined axes and revolution about the vertical axis, and means operable during the said combined rotation and revolution of the cylinders for preventing their further rotation at any desired time after the release of the brake, whereby the cylinders will thereafter revolve without rotation.

17. A machine of the character described having, in combination, a driven clutch member, a cooperating clutch member that may be actuated into engagement with the driven clutch member so as to be actuated therewith, a shaft, two cylinders each having end walls, the cylinders being carried by the respective ends of the shaft each at one of the end Walls, means controlled by the driven clutch member at a time when the cooperating clutch member is disengaged therefrom for rotating the shaft, means for actuating the cooperating clutch member into clutching engagement with the driven clutch member at any desired time, means connecting the shaft to the cooperating clutch member to revolve the shaft and the cylinders as a unit from the cooperating clutch member when the cooperating clutch member is in engagement with the driven clutch member, and means for preventing rotation of the shaft during its revolution.

18. A machine of the character described having, in combination, a cylinder rotatable about its axis to tumble its contents and revolvable about an axis external to the cylinder to extract liquid from the tumbled contents, means for simultaneously rotating the cylinder about its axis and revolving the cylinder about the external axis, and means for preventing rotation of the cylinder at any desired time during its simultaneous rotation and revolution.

JOHN E. VETORINO. NORMAN R. GENDRON. 

